MX2014011444A

MX2014011444A - System and method for recovery of waste heat from dual heat sources.

Info

Publication number: MX2014011444A
Application number: MX2014011444A
Authority: MX
Inventors: Vittorio Michelassi; Matthew Alexander Lehar
Original assignee: Gen Electric
Priority date: 2012-03-24
Filing date: 2013-03-15
Publication date: 2014-11-10
Also published as: EP2834477A1; CN104185717A; RU2014136932A; US20130247570A1; CA2867120C; US9038391B2; CA2867120A1; AU2013240243B2; AU2013240243A1; WO2013148297A1; CN104185717B

Abstract

A waste heat recovery system includes a heat recovery cycle system (10) coupled to at least two separate heat sources having different temperatures. The heat recovery cycle system is coupled to a first heat source (26) and at least one second heat source (52). The heat recovery cycle system is configured to circulate a working fluid. The at least one second heat source includes a lower temperature heat source than the first heat source. The working fluid is circulatable in heat exchange relationship through a first heat exchange unit (18) and a second heat exchange unit (20) for heating the working fluid in the heat recovery cycle system. The first heat exchange unit is coupled to the at least one second heat source to heat at least a portion of a cooled stream of working fluid to a substantially higher temperature.

Description

SYSTEM AND METHOD FOR RECOVERING RESIDUAL HEAT FROM DUAL HEAT SOURCES BACKGROUND OF THE INVENTION The embodiments described herein generally relate to the field of power generation and, more particularly, to a system and method for recovering waste heat from a plurality of heat sources having different temperatures for the generation of electricity.

Large amounts of waste heat are generated through a wide variety of industrial and commercial processes and operations. Exemplary waste heat sources include exhaust and heat flow from the space heating assemblies, steam boilers, motors and cooling systems. Many fuel burner engines, in addition to producing a high temperature exhaust flow, also emit heat at a lower temperature in lubricating oil, cooling fluid or compressor intermediate radiator air. Although the descent cycles can be used to recover additional electrical or shaft power from the hot exhaust gases emitted by the engine, they are generally configured to make efficient use of the lower temperature heat sources available.

When the residual heat is of low degree, such waste heat having a temperature below 300 degrees Celsius, for example, Conventional heat recovery systems do not operate with sufficient efficiency to make energy recovery cost-effective. The net result is that vast amounts of waste heat fall into the atmosphere, soil or water.

A method for generating waste heat electricity includes single-cycle systems or two-cycle systems that are used in heat recovery applications with residual heat sources or different temperature levels. The single-cycle configurations collect heat from different different waste heat locations in a series arrangement of heat exchange units with an intermediate heating fluid. This "multi-function" configuration decreases the maximum resulting fluid vapor temperature because the heat available from the heat sources of various temperature levels are mixed. An undesired result of this configuration is a reduced Carnot efficiency. In two cycle configurations, the hot heat source heats a high boiling liquid in an upper loop, and the cold heat source heats a low boiling liquid in a separate lower loop. Although, the two-cycle system generally achieves better performance than a single cycle, the components in the two-cycle system are more complex and require more components. As a result, the overall cost of the two cycle system is significantly higher.

In another conventional system provided to generate electricity from waste heat, a system of organic rankine cycles in Cascade for waste heat utilization includes a pair of organic Rankine cycle systems, which include two working fluids. The cycles are combined, and the respective organic working fluids are chosen in such a way that the organic working fluid of the first organic rankine cycle is condensed at a condensation temperature which is above the boiling point of the organic working fluid of the second cycle. organic. A single common heat exchange unit is used for both the condenser of the first organic rankine cycle system and the organic second rankine evaporator cycle. A cascade organic Rankine cycle system converts surplus heat within certain temperature ranges, but does not recover residual heat over a wide temperature range, due to a higher temperature limit in the organic fluid of approximately 250 ° C imposed by tendency to degrade quickly at higher temperatures.

It would be desirable to have a system that effectively recovers waste heat over a wide temperature range from multiple heat sources using a single working fluid.

BRIEF DESCRIPTION OF THE INVENTION According to an exemplary embodiment described herein, a waste heat recovery system including a heat generation system and a heat recovery system. The system of Heat generation includes at least two separate heat sources that have different temperatures. The at least two separate heat sources include a first heat source and at least a second heat source. The heat recovery system is configured to circulate a single working fluid, and includes a heater, a first heat exchange unit and a second heat exchange unit. The heater is configured to circulate a working fluid in heat exchange relationship with a hot fluid to evaporate the working fluid. The first heat exchange unit is coupled to the heater, where the vaporized working fluid can circulate in heat exchange relationship through the first heat exchange unit to heat at least a portion of the working fluid in the heat exchanger. system of heat recovery cycles. At least a portion of the working fluid can be circulated in heat exchange relationship through the second heat exchange unit to heat at least a portion of the working fluid in the heat recovery cycle system. The heat recovery cycle system is coupled to a first heat source between at least two separate heat sources and at least one second heat source between at least two separate heat sources. The heat recovery cycle system is configured to remove heat from the first heat source and the second heat source.

According to an exemplary embodiment described herein, a waste heat recovery system includes a combustion engine and a system of heat recovery cycles. The combustion engine includes a heat source having an engine exhaust unit and at least one additional heat source selected from the group comprising a lower temperature intermediate radiator, a higher temperature intermediate radiator, an exhaust unit of low pressure compressor or combination of these. The heat source comprises a heat source of higher temperature than the at least one additional heat source. The heat recovery cycle system includes a heater, a cooling unit, at least two expanders, a first heat exchange unit and a second heat exchange unit. The heat recovery cycle system is coupled to the engine exhaust unit and the at least one additional heat source and is configured to circulate a working fluid. The first heat exchange unit is coupled to the heater and the at least one additional heat source, wherein at least a portion of the working fluid can circulate in heat exchange relationship through the first heat exchange unit. heat to heat the working fluid in the heat recovery cycle system. At least a portion of the working fluid can be circulated in heat exchange relationship through the second heat exchange unit to heat the working fluid in the heat recovery cycle system. The heat recovery cycle system is configured to remove heat from the engine exhaust unit and the at least one additional heat source.

According to an exemplary embodiment described herein, a residual heat recovery system includes a combustion engine and a heat recovery cycle system. The combustion engine includes a heat source having an engine exhaust unit and at least one additional heat source selected from the group comprising a lower temperature intermediate radiator, a higher temperature intermediate radiator, a low pressure compressor exhaust unit or combination of these. The heat source and the at least one additional heat source with different temperatures, wherein the at least one source comprises a heat source of temperature greater than the at least one additional heat source. The heat recovery cycle system includes a heater and at least two expanders coupled to at least one generator unit, a first heat exchange unit and a second heat exchange unit. The heater is coupled to the engine exhaust unit. The heat recovery cycle system is configured to circulate a working fluid. The working fluid comprises carbon dioxide (C02). The first heat exchange unit is coupled to the heater and at least one additional heat source. At least a portion of the working fluid can be circulated in heat exchange relationship through the first heat exchange unit to heat the working fluid in the heat recovery cycle system. At least a portion of the working fluid can be circulated in heat exchange relationship through the second heat exchange unit to heat the working fluid in the heat recovery cycle system. The heat recovery cycle system is configured to remove heat from the engine exhaust unit and the at least one additional heat source.

Various refinements of the features noted above exist in relation to various aspects of the present disclosure. Additional features can also be incorporated in these various aspects. These refinements and additional features may exist individually or in any combination. For example, the different features mentioned below in relation to one or more embodiments illustrated may be incorporated in any aspect described above of the present description alone or in any combination. Again, the brief description of the invention presented above is intended to familiarize the reader with certain aspects and contexts of the present description without limitation to the subject claimed.

BRIEF DESCRIPTION OF THE FIGURES These and other features, aspects and advantages of the present disclosure will be better understood when reading the following detailed description with reference to the accompanying drawings, where: Figure 1 is a graphic representation of a residual heat recovery system according to an exemplary embodiment described herein.

DETAILED DESCRIPTION OF THE INVENTION In accordance with the embodiment described herein, a system of heat recovery cycles for recovering residual heat from dual sources is described. The exemplary heat recovery cycle system includes a heater configured to circulate a working fluid in heat exchange relationship with a hot fluid to vaporize the working fluid. The heat recovery cycle system includes a first heat exchange unit configured to circulate a first vaporized flow rate of the heater's working fluid in heat exchange ratio with a first portion of a cooled flow of the working fluid for heating the first portion of the cooled flow of the working fluid. The heat recovery cycle system includes a second heat exchange unit configured to circulate a second vaporized flow rate of the working fluid in heat exchange ratio with a second portion of a cooled flow rate of the working fluid, to heat the second portion of the cooled flow of the working fluid before re-supplying the heater. In accordance with the exemplary embodiment of the present disclosure, the cycle system of Heat recovery is integrated with a first heat source and a second heat source to allow a more efficient recovery of waste heat for the generation of electricity. The first and second heat sources may include combustion engines, gas turbines, thermal, industrial and residential heat sources or the like.

Referring to Figure 1, a system of heat recovery cycles 10 is illustrated in accordance with an exemplary embodiment of the present disclosure. The illustrated heat recovery cycle system 10 includes a heater 12, a first expander 14, a second expander 16, a first heat exchange unit or recuperator 18 and a second heat exchange unit or recuperator 20, a unit refrigeration 22 and a pump 24. A single working fluid is circulated through the system of heat recovery cycles 10.

The heater 12 is coupled to a first heat source 26. In the illustrated embodiment, the heater 12 is coupled to a motor 28 and more particularly to an engine exhaust unit such as a power turbine 30 of the engine 28. heater 12 is configured to receive a high temperature exhaust flow 32 that originates from the discharge of the power turbine 30. The heater 12 receives heat from the high pressure exhaust flow 32 generated from the power turbine 30 and heats a working fluid to generate a first vaporized flow 34 of the working fluid. More specifically, the working fluid is heated at an elevated pressure to a superheated state in the heater 12 by the exhaust flow rate. high temperature 32. The first vaporized flow rate 34 of the working fluid is passed through the first expander 18 to expand the first vaporized flow rate 34 of the working fluid at a lower pressure and to activate a generator unit 36 by means of an axis 38. The first expander 18 can be an axial type expander, a pulse type expander, a high temperature screw type expander or a radial inlet turbine type expander. After passing through the first expander 18, the first vaporized flow 34 of the working fluid, discharged at a relatively lower pressure and lower temperature, is passed through the first heat exchange unit or recuperator 18 to the refrigeration unit. . The vaporized flow rate 34 is cooled to near ambient temperature in the first heat exchange unit 18. The first vaporized flow rate 34 is further cooled and may be condensed in a liquid or a dense supercritical state suitable for pumping, in the refrigeration unit 22, to generate a cooled flow 40 of the working fluid. The cooled flow 40 of the working fluid is then pumped using the pump 24 for a control valve 42 whereby the cooled flow rate 40 is divided into two flow rates: a first portion 44 and a second portion 46. In one embodiment, the first vaporized stream 34 can be supercritically cooled to a supercritical fluid in dense phase before pumping it upwardly under pressure.

The first portion 44 of the cooled flow 40 returns to the heater 12 by means of the second heat exchange unit, recuperator 20. In the illustrated embodiment, the control valve 42 is coupled between the first heat exchange unit 18 and the second heat exchange unit 20 and is configured to control the flow of the cooled flow 40 of the refrigeration unit 22 to the first heat exchange unit 18 and the second heat exchange unit 20 during the operation of the system which depends on the additional heat provided by a second heat source (described herein).

The second portion 46 of the cooled flow rate 40 returns to the first heat exchange unit 18 where it is heated to an intermediate temperature of the discharge of the first expander 14 and more in particular to the temperature of the first vaporized flow rate 34 to undergo a second expansion to through the second expander 16. More specifically, the first heat exchange unit 18 is configured to circulate the first vaporized flow rate 34 of the working fluid of the first expander 14 in the heat exchange ratio with the second portion 46 of the flow rate cooled 40 of the working fluid to heat the second portion 46 of the cooled flow 40 of the working fluid and generate a second vaporized flow rate 48 of the working fluid. The heat transferred from the first vaporized flow rate 34 to the second portion 46 of the cooled flow rate 40 in the first heat exchange unit 18 can be supplemented by supplementary heat from a complementary intermediate radiator air flow rate 50 having a temperature that can be compared to the first vaporized flow rate 34 in the discharge of the first expander 14. In this example in particular, the supplementary heat is provided by the air flow of the supplementary intermediate radiator 50, discharged from a second heat source 52, and more in particular a discharge air flow of the motor 28. As better illustrated in FIG. 1, the air flow of the complementary intermediate radiator 50 originates from a low pressure compressor exhaust unit and more in particular a low pressure compressor discharge 54 in the engine 28. The larger the amount of heat available from the flow rate. of supplementary intermediate radiator 50, the larger the proportion of the cooled flow rate 40 that can be channeled through the control valve 42 to the first heat exchange unit 18 more than to the second heat exchange unit 20. The heat of the first heat source 26 and the second heat source 52 can be optimally used by adjusting the radius of flow in the control valve 42.

The second vaporized flow rate 48 of the working fluid is passed through the second expander 16 to expand the second vaporized flow rate 48 of the working fluid and to activate a second generator unit (not shown) or the first generator unit 36 by means of of the shaft 38. The second expander 16 may be an axial expander, a pulse type expander, a high temperature screw type expander or a radial inlet turbine type expander. After passing through the second expander 16, the second vaporized flow rate 48 of the working fluid passes through the second heat exchange unit 20 and back to the cooling unit 22. The second heat exchange unit 20 is configured to circulate the second vaporized flow rate 48 of the working fluid of the second expander 16 in heat exchange relation with the first portion 44 of the cooled flow 40 of the working fluid to heat the first portion 44 of the working fluid before being supplied to the heater 12. A second control valve 56 is coupled between the first heat exchange unit 18 and the second heat exchange unit 20 and configured to control the flow of the second vaporized flow rate 48 of the second expander 16 and the first vaporized flow rate. 34 of the first expander 14 to the refrigeration unit 22. The second vaporized flow rate 48 of the working fluid is combined by means of the second control valve 56 with the first vaporized flow rate 34 before reaching the cooling unit 22. The first flow vaporized 34 and the second vaporized flow rate 48 combined are cooled to generate the cooled flow 40 of the working fluid. The cooled flow 40 of the working fluid is then pumped using the pump 24 for the heater 12 by means of the second heat exchange unit 20 (as described above) or for the second expander 16 by means of the first exchange unit of heat 18 (as described above). The cycle can then be repeated.

The heat recovery cycle system 10 may further include an intermediate radiator 58 coupled to the first heat exchange unit 18 and the air flow of the supplemental intermediate radiator 50 and a gasket cooler 60 coupled to the intermediate radiator 58 and the engine 28 In the illustrated embodiment, there are two examples of heat exchange (also referred to as intracyclic heat transfer between a high pressure flow of the working fluid and a low pressure flow rate of the working fluid) In the first example, the first flow vaporized 34 of the working fluid is circulated in heat exchange ratio with the second portion 46 of the cooled flow rate 40 of the working fluid to heat the second portion 46 of the cooled flow 40 of the working fluid and generate the second vaporized flow rate 48 of the fluid This exchange of heat serves to boil or otherwise increase the enthalpy (if the second portion 46 of the cooled flow 40 of the working fluid is at a subcritical temperature) of the second portion 46 of the cooled flow 40 of the working fluid , so that the second vaporized flow rate 48 of the working fluid can then undergo another expansion in the second turbine 16. In the second example, the The vaporized flow rate 48 of the working fluid of the second expander 16 is circulated in heat exchange relation with the first portion 44 of the cooled flow 40 of the working fluid to heat the first portion 44 of the cooled flow 40 of the working fluid. The first portion 44 of the cooled flow 40 of the working fluid is to supply the heater 12 and heated using the first heat source 26 to complete the flow circuit. The first heat exchange unit 18 and the second heat exchange unit 20 function as "recuperators" in the system 10.

The first heat exchange unit 18 is described as coupled to any one or more of the second heat sources 52 such as the discharge flow of the low pressure compressor 54. Such second heat sources 52 are also commonly coupled to the engine 28. The one or more second heat sources 52 are configured to provide additional heat or to partially vaporize (with "or" as the second portion 46 of the cooled flow 40 of the working fluid is used here. More particularly, the second portion 46 of the cooled flow 40 of the working fluid is passed through the heat exchange unit 18 which in conjunction with the intermediate radiator 58 provides heat and / or evaporation or even overheating of the second portion 46 of the cooled flow 40 of the working fluid. In one embodiment, the first heat exchange unit 18 is coupled to at least two second heat sources 52 with the at least two second heat sources 52 which are coupled in series or in parallel. It should be noted that the second heat source 52 includes a heat source of lower temperature than the first heat source 26. In one example, the temperature of the second heat source 52 can be in the range of 80 to 300 degrees Celsius. It should be noted that in other exemplary embodiments, the first and second heat sources 26, 52 may include multiple other low grade heat sources such as gas turbines with intermediate radiators. The first heat exchange unit 18 receives heat from the first vaporized stream 34 and generates the second vaporized stream 48. In one example, the second vaporized stream 48 may be at a pressure of 250 bar and a temperature of about 250 degrees Celsius. The second vaporized flow 48 is passed through the second expander 16. In the illustrated embodiment, the first expander 14 and the second expander 16 are coupled to the single generator unit 36 via the axis 28. In certain other exemplary embodiments, the second expander 16 (which in one example comprises a screw type compressor) can be configured to activate a second generator unit (not shown).

The polished arrangement of the second heat source 52 facilitates the removal of effective heat from the plurality of motor heat sources at a lower temperature. This increases the effectiveness of refrigeration systems and provides effective conversion of waste heat into electricity.

In the illustrated embodiment, the working fluid includes carbon dioxide. The use of carbon dioxide as the working fluid has the advantage of being non-infallible, non-corrosive and capable of withstanding higher cyclic temperatures (for example above 400 degrees Celsius). In an embodiment as described above, carbon dioxide can be heated supercritical at temperatures substantially without the risk of chemical decomposition. The transfer of two different intra-cycles of heat after an initial expansion of the working fluid allows the working fluid to produce more work through successive expansions than would be possible with a single expansion process (as in the operation conventional Rankine cycles). In other modalities, other work fluids are also conceived.

Referring again to Figure 1, in the illustrated waste heat recovery system 10, in one example, the temperature of the high pressure exhaust flow 32 of the first heat source 26 of the engine 28 can be on the temperature scale from 450 to 500 degrees Celsius. The heater 12 receives heat from the high pressure exhaust flow 32 generated from the first heat source 26 and generates a working fluid vapor as the first vaporized flow rate 34. In one example, the first vaporized flow rate 34 may be at a pressure of 250 bar and temperature of approximately 450 degrees Celsius. The first vaporized stream 34 is passed through a first expander 14 (which in one example comprises a radial time expander) for driving the generator unit 36. After passing through the first expander 14, the first vaporized flow rate 34 is passed through the first heat exchange unit 18 and then condensed in a liquid in the cooling unit 22 to form the cooled flow rate 40 which is then pumped by a pump 24 to the control valve 42. In one example, the first vaporized flow rate 34 can be supplied to the refrigeration unit 22 at a pressure of 80 bar and 70 degrees Celsius. In one example, the second portion 46 of the cooled flow rate 40 can be supplied to the first heat exchange unit 18 at a pressure of 250 bar and 50 degrees Celsius. In an example, the first portion 44 of the cooled flow 40 can be supplied to the second heat exchange unit 20 at a pressure of 250 bar and 50 degrees Celsius. In one example, the second vaporized flow rate 48 of the first heat exchange unit 18 is supplied to the second expander 16 at a pressure of approximately 250 bar and a temperature of approximately 350 degrees Celsius. In one example, the air flow of the supplementary intermediate radiator 50 of the second heat source 52 is provided as a low temperature air flow and can be supplied to the intermediate radiator 58 at a pressure of 3 bar and an approximate temperature of 250 degrees. Celsius. In one example, the air flow of the intermediate radiator 62 of the intermediate radiator 58 is provided as a low temperature air flow and can be supplied to the optional trim cooler 60 and back to the engine 28 at a pressure of 3 bar and a temperature Approximately 70 degrees Celsius. It should be noted herein that the temperature and pressure values mentioned above are exemplary values and should not be construed as limiting values. The values may vary depending on the applications.

As mentioned above, after passing through the first expander 14, the first vaporized flow rate 34 of the working fluid at a relatively lower pressure and lower temperature is passed through the first heat exchange unit 18 to the unit refrigeration 22. The refrigeration unit 22 is explained in greater detail herein. In the illustrated embodiment, the refrigeration unit 22 is a cooled air unit. The second vaporized flow rate 34 of the working fluid exiting through the second heat exchange unit 18 is passed through the air cooler of the cooling unit 22 (not shown). The cooler of air 22 is configured to cool the first vaporized flow rate 34 of the working fluid using ambient air.

In conventional systems, it may not be possible to condense carbon dioxide in many geographic locations if the ambient air is used as a cooling medium for a refrigeration unit, since the ambient temperatures in such geographical locations routinely exceed the critical temperature of carbon dioxide. In accordance with the embodiments of the present disclosure, the carbon dioxide may or may not condense depending on the circumstances. The described system operates in a similar manner when there is no condensation, except that the fluid simply cools supercritically to a supercritical fluid of dense phase before pumping it under pressure.

As mentioned above, after passing through the second expander 16, the second vaporized flow rate 48 of the working fluid passes through the second heat exchange unit 20 to the refrigeration unit 22. The second vaporized flow rate 48 of the fluid Working flow through the second heat exchange unit 20 is passed through the air cooler of the cooling unit 22. In a manner similar to the cooling of the first vaporized flow rate 34, the air cooler is configured to cool , and can vaporize the second vaporized flow 48 of the working fluid using the ambient air.

Although the above modalities are mentioned with reference to carbon dioxide as the working fluid, in certain embodiments, other low critical temperature working fluids suitable for heat recovery cycle systems, such as a Rankine cycle or Brayton cycle, are also conceived. As mentioned herein, ensuring the availability of a refrigerant flow for the heat recovery cycle facilitates the availability of an adequate refrigerant flow to cool the working fluid as the ambient cooling temperature increases during the summer season. According to the exemplary embodiment, the cooling unit and the low pressure stage of the turbine are reduced in volume for the heat recovery cycles using carbon dioxide as the working fluid. The exemplary heat recovery cycle system as described hereinBy employing dual residual heat sources at different temperatures, more than just a source of high temperature waste heat, it provides a system capable of significantly greater energy output. Also, the exemplary heat recovery cycle using a dual heat source input as described herein has a compact fingerprint and consequently is faster upstream than heat recovery cycles using steam as the work fluid.

Although only certain features of the described embodiment have been illustrated and described herein, many modifications and changes will occur to those skilled in the art. Therefore, it should be understood that the appended claims are intended to cover such modifications and changes that are within the scope of the description.

Claims

NOVELTY OF THE INVENTION CLAIMS

1 . A waste heat recovery system comprising: a heat generation system comprising at least two separate heat sources having different temperatures, wherein the at least two separate heat sources comprise a first heat source and at least a second source of heat; a heat recovery system configured to circulate a single working fluid, the heat recovery cycle system comprises: a heater, configured to circulate a working fluid in heat exchange relationship with a hot fluid to vaporize the work fluid; a first heat exchange unit coupled to the heater, wherein the vaporized working fluid can circulate in heat exchange relationship through the first heat exchange unit to heat at least a portion of the working fluid in the system of heat recovery cycles; and a second heat exchange unit, wherein at least a portion of the working fluid can circulate in heat exchange relationship through the second heat exchange unit to heat at least a portion of the working fluid in the heat recovery cycle system, where the heat recovery cycle system is coupled to a first heat source between at least two sources of heat separate heat and at least one second heat source between at least two separate heat sources, and wherein the heat recovery cycle system is configured to remove heat from the first heat source and the second heat source.

2. The recovery system according to claim 1, further characterized in that a single working fluid comprises carbon dioxide (C02).

3. The recovery system according to claim 1, further characterized in that the first heat exchange unit is coupled to the at least one second heat source, and wherein the at least one second heat source is selected from a group comprising a lower temperature intermediate radiator, a higher temperature intermediate radiator, a low pressure compressor exhaust unit or combinations thereof.

4. The recovery system according to claim 1, further characterized in that at least a second heat source is configured to at least partially heat a portion of a cooled flow of the working fluid.

5. The recovery system according to claim 1, further characterized in that the first heat exchange unit is configured to receive an intermediate radiator air complementary to the at least one second heat source to heat at least a portion of a cooled flow rate of the Work at a substantially higher temperature before entering an expander.

6. The recovery system according to claim 1, further characterized in that the first heat source comprises an engine exhaust unit.

7. The recovery system according to claim 1, further characterized in that it further comprises a first expander in fluid communication with the heater, wherein the first expander comprises at least one of a radial type expander, an axial type expander, an expander screw type or an impulse type expander.

8. The recovery system according to claim 7, further characterized in that it additionally comprises a second expander in fluid communication with the heater, wherein the second expander comprises at least one of a radial type expander, an axial type expander, a Screw type expander or impulse type expander.

9. The recovery system according to claim 8, further characterized in that the first heat exchange unit is coupled to the second expander and configured to heat at least a portion of a cooled flow of working fluid to a substantially higher temperature prior to enter the second expander.

10. The recovery system according to claim 8, further characterized in that the first expander and the second expander are coupled to a generator unit.

The recovery system according to claim 8, further characterized in that the first expander is coupled to a first generator unit and the second expander is coupled to a second generator unit.

12. The recovery system according to claim 1, further characterized by additionally comprising a cooling unit, wherein the working fluid of the heat exchange unit is supplied through the cooling unit.

13. The recovery system according to claim 12, further characterized in that it additionally comprises a pump located between the cooling unit and the first heat exchange unit and the second heat exchange unit.

14. The recovery system according to claim 13, further characterized in that it additionally comprises a first control valve placed in a flow path between the first heat exchange unit and the second heat exchange unit, the control valve can be in operation to control a flow of a cooled flow of working fluid entering the first heat exchange unit and the second heat exchange unit.

15. The recovery system according to claim 14, further characterized in that it additionally comprises a second control valve placed in a flow path between the first heat exchange unit and the second heat exchange unit, the control valve can be in operation to control a flow of a first vaporized flow of working fluid and a second vaporized flow of working fluid entering the cooling unit.

16. The recovery system according to claim 1, further characterized in that the heat generation system comprises a combustion engine.

17. A waste heat recovery system comprising: a combustion engine comprising a heat source having an engine exhaust unit and at least one additional heat source selected from the group comprising a lower temperature intermediate radiator, a Higher temperature intermediate radiator, a low pressure compressor exhaust unit or combination thereof, a heat source comprises a temperature source of higher temperature than at least one additional heat source; a system of heat recovery cycles comprising: a heater, a refrigeration unit and at least two expanders, wherein the system of heat recovery cycles is coupled to the engine exhaust unit and at least one source of additional heat and configured to circulate a working fluid; a first heat exchange unit coupled to the heater and so less an additional heat source, wherein at least a portion of the working fluid can circulate in heat exchange relationship through the first heat exchange unit to heat the working fluid in the recovery cycle system of hot; and a second heat exchange unit, wherein at least a portion of the working fluid can circulate in heat exchange relationship through the second heat exchange unit to heat the working fluid in the cycle system of heat. heat recovery, wherein the heat recovery cycle system is configured to remove heat from the engine exhaust unit and the at least one additional heat source.

18. The recovery system according to claim 17, further characterized in that the working fluid comprises carbon dioxide (C02).

19. The recovery system according to claim 17, further characterized in that the heater is coupled to the first heat source.

20. The recovery system according to claim 17, further characterized in that at least one additional heat source is configured to heat at least a portion of a cooled flow rate of the working fluid.

21. The recovery system according to claim 20, further characterized in that the first heat exchange unit is coupled to the second expander and configured to heating a portion of the cooled flow of working fluid to a substantially higher temperature before entering the second expander.

22. The recovery system according to claim 17, further characterized in that the first heat exchange unit is configured to receive an intermediate radiator air complementary to the at least one second heat source to heat at least a portion of the flow rate cooling the working fluid to a substantially higher temperature before entering the second expander.

23. The recovery system according to claim 17, further characterized in that it further comprises a pump, wherein the pump is located between the cooling unit and the first heat exchange unit and the second heat exchange unit.

24. The recovery system according to claim 17, further characterized in that it additionally comprises a first control valve placed in a flow path between the first heat exchange unit and the second heat exchange unit, the control valve can be in operation to control a flow of a cooled flow of working fluid entering the first heat exchange unit and the second heat exchange unit.

25. The recovery system according to claim 17, further characterized in that the first expander and the second expander are coupled to at least one generator unit.

26. A waste heat recovery system comprising: a combustion engine comprising a heat source having an engine exhaust unit and at least one additional heat source selected from the group comprising a lower temperature intermediate radiator, a intermediate temperature radiator, a low pressure compressor exhaust unit or combination of these, the heat source and the at least one additional heat source have different temperatures, wherein the heat source comprises a temperature heat source greater than the at least one additional heat source; a system of heat recovery cycles comprising: a heater and at least two expanders coupled to at least one generator unit, wherein the heater is coupled to the engine exhaust unit, the system of recovery cycles of heat is configured to circulate a working fluid, and wherein the working fluid comprises carbon dioxide (C02); a first heat exchange unit coupled to the heater and at least one additional heat source, wherein at least a portion of the working fluid can circulate in heat exchange relationship through the first heat exchange unit for heat the working fluid in the heat recovery cycle system; and a second heat exchange unit, where at least a portion of the working fluid can circulate in heat exchange relationship through the second heat exchange unit to heat the working fluid in the heat recovery cycle system, where the system of heat recovery cycles it is configured to remove heat from the engine exhaust unit and the at least one additional heat source.